CN101865253B

CN101865253B - Double clutch transmission

Info

Publication number: CN101865253B
Application number: CN2010101638971A
Authority: CN
Inventors: W·里格尔; P·雷克; G·贡波尔茨贝格
Original assignee: ZF Friedrichshafen AG
Current assignee: ZF Friedrichshafen AG
Priority date: 2009-04-14
Filing date: 2010-04-13
Publication date: 2013-07-03
Anticipated expiration: 2030-04-13
Also published as: DE102009002343B4; US20100257956A1; CN101865253A; US8365625B2; DE102009002343A1

Abstract

A double clutch transmission comprising two clutches each having an input side connected to a drive shaft and an output side connected to one of two transmission input shafts coaxially arranged with respect to one another. At least two countershafts, on which toothed idler gearwheels are pivotally supported and toothed fixed gearwheels are disposed on both transmission input shafts in a rotationally fixed manner and mesh with at least some of the idler gearwheels. A plurality of coupling devices connect an idler gearwheel to a countershaft in a rotationally fixed manner. One output gear is provided on both countershafts which is coupled to gearing of an output shaft. At least one first shift element connects two toothed gearwheels in a rotationally fixed manner such that a plurality of power shifting forward gears and at least one reverse gear can be shifted.

Description

Dual-clutch transmission

Technical field

The present invention relates to a kind of dual-clutch transmission.

Background technique

Dual-clutch transmission by known six retainings of file DE 103 05 241 A1 or seven retainings.This dual-clutch transmission comprises two clutches, described two clutches be connected with live axle with its input side respectively and with its outlet side respectively with two transmission input shafts in one be connected.Two transmission input shafts arrange coaxially with each other.Two other jack shaft is arranged to axis and is parallel to two transmission input shafts, the free gear of described two jack shafts and the engagement of the fixed gear of transmission input shaft.In addition coupling can move axially the ground rotationally fixedly be fixed on the jack shaft, in order to can connect corresponding shift gear.The velocity ratio of corresponding selection is delivered on the differential mechanism by output gear.In order to realize the gear stage of expectation in known dual-clutch transmission, many gears plane is necessary, makes that needing when mounted is not inapparent structure space.

In addition by the known cylindrical gears formula of file DE 38 22 330 A1 speed changer.This cylindrical gears formula speed changer comprises the double clutch that can shift gears under load, its part is connected with live axle and its another part is connected with driving hollow shaft on can be rotated to support on live axle.For the velocity ratio of determining, live axle can be coupled by switching member and driving hollow shaft.

By the known power-shift transmission with two clutches of file DE 10 2,004 001 961 A1, described two clutches are equipped on a speed changer part respectively.The transmission input shaft of two speed changer parts arranges coaxially with each other and meshes by the free gear of fixed gear with the jack shaft that sets.The corresponding free gear of each jack shaft can be connected with corresponding jack shaft by means of the switching member rotationally fixedly that sets.In addition, by known a kind of eight shift transmissions of this document, an other switching member wherein is set is used for being coupled two transmission input shafts to realize other gear stage.Eight shift transmissions need at least six gear planes in two speed changer parts in this design proposal, in order to can realize each gear stage.This causes structure length to prolong undesirably vertically, has made significant limitation and has been installed to installation possibility in the car.

Disclose another kind of power-shift transmission by patent documentation DE10 2,005 028 532 A1 in addition, it comprises two input shafts and jack shaft only.In this design proposal, for example nine shift transmissions need at least seven gear planes, in order to can realize gear stage.This causes structure length undesirably to prolong in the axial direction.For realizing that back gear ratio need have the additional shaft on a gear plane, it comprises a switching member and two gears in addition.Another shortcoming in the known power-shift transmission is only can carry out power gear shifting between first and second retainings.

Summary of the invention

The objective of the invention is to, advise a kind of dual-clutch transmission that starts described type, wherein under little structure space demand, realize the gear stage that a plurality of motilities are shifted gears as far as possible economically and with the least possible member.

According to the present invention, this purpose solves by the dual-clutch transmission with following feature.Dual-clutch transmission comprises: two clutches, the input side of described two clutches be connected with a live axle and the outlet side of described two clutches respectively with two transmission input shafts that arrange coaxially with each other in one be connected; Two jack shafts, the shift gear that constitutes free gear can be rotated to support on the described jack shaft; Rotationally fixedly is arranged on described two transmission input shafts and constitutes shift gear fixed gear, the engagement of at least part of and free gear; A plurality of be used to the coupling that free gear is connected with the jack shaft rotationally fixedly; Be arranged on each output gear on two jack shafts, this output gear correspondingly is coupled with the tooth portion of a driven shaft; And at least one is for the switching member of two shift gears of rotationally fixedly connection, and the forward gear that wherein can connect a plurality of motilities gearshifts reverses gear with at least one; It is characterized in that, five gear planes are set, at least four bidentate wheel planes wherein are set, and each free gear of first and second jack shafts is equipped on a fixed gear of one of described transmission input shaft in each bidentate wheel plane, wherein at least one free gear can be used at least two gears in each bidentate wheel plane, makes the circuitous retaining of at least one motility gearshift to connect by described at least one switching member.

Accordingly, advise dual-clutch transmission a kind of structure space optimization, that have two clutches, the input side of described two clutches be connected with a live axle and the outlet side of described two clutches respectively with two transmission input shafts that for example arrange coaxially with each other in one be connected.Dual-clutch transmission comprises two jack shafts or analog, the shift gear that constitutes free gear can be rotated to support on the described jack shaft, wherein is provided with rotationally fixedly and is arranged on described two transmission input shafts and constitutes shift gear fixed gear, the engagement of at least part of and free gear.In addition, be provided with a plurality of be used to the coupling that free gear is connected with the jack shaft rotationally fixedly.Have according to dual-clutch transmission of the present invention: be arranged on each output gear or constant small gear (Konstantenritzel) on each described jack shaft, this output gear or this constant small gear correspondingly are coupled with the tooth portion of a driven shaft, so that corresponding jack shaft is connected with output unit; And at least one is that can activate or can be closed, as so-called circuitous retaining-switching member, be used for switching member or analog that rotationally fixedly connects two shift gears, wherein can connect the forward gear of a plurality of motilities gearshifts and reversing gear of at least one motility gearshift.

According to the present invention, the dual-clutch transmission of advising preferably comprises only five gear planes, can realize the forward gear of at least nine motility gearshifts with little structure space demand by these gear planes.

At least four bidentate wheel planes for example can be set, and each free gear of first and second jack shafts is equipped on a fixed gear of one of transmission input shaft in each bidentate wheel plane, wherein, at least one free gear can be used at least two gears in each bidentate wheel plane, makes the circuitous retaining of at least one motility gearshift to connect by at least one switching member.Owing to the possible multiple utilization of free gear, in the dual-clutch transmission of advising, realize the velocity ratio of maximum quantity with the least possible gear plane, wherein preferred all forward gears are the motility gearshifts with reversing gear when carrying out in order.

For by optimizing speed ratio (Abstufung) at interval in the dual-clutch transmission as suggested in the present invention, for example also can substitute another bidentate wheel plane like this by two individual gears planes, namely substitute a fixed gear by two fixed gears.Can realize special coordination, progressive gear speed ratio thus at interval.

The dual-clutch transmission of advising can preferably constitute nine shift transmissions, has the gear level of at least nine motility gearshifts.Owing to be the mode of structure of lacking with respect to known gearbox arrangement, be particularly useful for front cross mounting type in vehicle by dual-clutch transmission of the present invention.But different according to the type of the vehicle of corresponding consideration and structure space situation, other mounting type also is possible.

Preferably, in the dual-clutch transmission of advising, the highest forward gear of first forward gear and/or motility gearshift can be circuitous retaining.In addition, at least one reverses gear and can constitute circuitous retaining equally.First jack shaft for example can be equipped with for example five free gears that can connect, and second jack shaft is equipped with for example four or five free gears that can connect, described free gear respectively with the engagement of the fixed gear of the transmission input shaft that sets.

When last or penult transmission gear speed ratio when (Gangsprung) designs more higherly at interval than the transmission gear ratio of corresponding front at interval, then by driver requested downshift the time, can obtain especially high output torque or driving power.

Can set in a kind of framework of possible embodiment, the dual-clutch transmission of advising also only comprises bidentate wheel plane.Only for example also can consider to arrange four bidentates wheel planes and for example individual gears plane.Other situation also is possible.

Can set according to the present invention, by at least one first switching member on first jack shaft, a free gear of second speed changer part can be connected with a free gear of first speed changer part, wherein, at least can corresponding connection first forward gear and the circuitous retaining of at least one overgear conduct by first switching member.

A kind ofly expand that design is also possible to be according to of the present invention, can connect the 9th forward gear and one by the switching member on first jack shaft and reverse gear as circuitous retaining.

Can set in addition, by substituting or additional switching member on second jack shaft, the free gear of second speed changer part can be connected with the free gear of first speed changer part, can connect by this switching member therefore that the 9th forward gear and one are reversed gear and/or the retaining of creeping keeps off as circuitous.

Therefore, by realizing circuitous retaining by described at least one switching member at least by dual-clutch transmission of the present invention, the shift gear of two speed changer parts is coupled mutually in these circuitous retainings, in order to realize the power stream by two speed changer parts thus.At this, the switching member of corresponding use is used for being coupled two free gears, and makes transmission input shaft interrelated thus.

In dual-clutch transmission, the layout that is used for being coupled the switching member of two definite free gears can change, so switching member needn't be forced to be arranged between the free gear that will be coupled.Also can consider other position of corresponding switching member accordingly, in order to for example optimize the connection on actuating device.

According to a kind of possible design proposal, in dual-clutch transmission, can set, as the first gear plane on bidentate wheel plane be included in two fixed gears on second transmission input shaft of second speed changer part as the second gear plane on bidentate wheel plane equally, wherein, as bidentate wheel plane or as the 3rd gear plane on individual gears plane, as the 4th gear plane on bidentate wheel plane with as bidentate wheel plane or be included in three fixed gears on first transmission input shaft of first speed changer part as the 5th gear plane on individual gears plane.

In the framework of another embodiment of the present invention, also can set, in the dual-clutch transmission of advising, as bidentate wheel plane or as the first gear plane on individual gears plane, as the second gear plane on bidentate wheel plane or individual gears plane be included in three fixed gears on second transmission input shaft of second speed changer part as the 3rd gear plane on bidentate wheel plane, wherein, as the 4th gear plane on bidentate wheel plane with comprise two fixed gears of first transmission input shaft of first speed changer part as the 5th gear plane on bidentate wheel plane.

Reverse to realize reversing gear for essential rotating speed is set in by dual-clutch transmission of the present invention, can for example use at least one intermediate gear or the analog that for example are arranged on the countershaft.One of free gear of a jack shaft also can be used as intermediate gear and reverses gear at least one.Just do not need the countershaft that adds for back gear ratio because one of free gear not only with a fixed gear and also with another free gear that can connect engagement of another jack shaft.Thereby be arranged on the jack shaft as the free gear that can connect and be used for realize that in addition another reverses gear at least for the essential intermediate gear that reverses gear.Intermediate gear is arranged on jack shaft with it still irrespectively also can constitute cone pulley on the additional countershaft.Intermediate gear also can not be arranged on the jack shaft that has existed, but for example is arranged on another independent axle, the 3rd jack shaft.

For the gear stage that obtains expecting, in by dual-clutch transmission of the present invention, can set, coupling or the analog of at least one two-sided action is set at each jack shaft.The coupling of setting can be connected with the jack shaft rotationally fixedly by the corresponding free gear that sets that makes of different situations according to steering in that be activated or closed state.Coupling or the analog of one-sided effect can also be set at least one described jack shaft in addition.For example the blade tooth clutch that hydraulic pressure, electricity, pneumatic, mechanically operated clutch or shape are sealed and the synchronization structure of variety of way can both be used as coupling, and they are used for rotationally fixedly and connect a free gear and a jack shaft.The coupling of a two-sided action can replace by the coupling of two one-sided effects, and vice versa.

Can consider, change shift gear description the layout possibility and also change the quantity of shift gear and the quantity of coupling, in order to realize that in the dual-clutch transmission of suggestion other gear, structure space the motility gearshift or can not power gear shifting be saved and member is saved.Especially the fixed gear on bidentate wheel plane can be divided into two fixed gears for two individual gears planes.Therefore improved transmission gear ratio at interval.Can exchange jack shaft in addition.Two speed changer parts also can exchange, and namely form mirror image around vertical axis.At this exchange hollow shaft and solid shaft.For example the gear of minimum can be arranged on the solid shaft thus, in order to continue to optimize the utilization of the structure space that exists.Can exchange adjacent gear plane in addition, for example in order to optimize bending shaft and/or connect the control actuating device best.In addition, can change the corresponding position of coupling on the gear plane.Also can change the action direction of coupling in addition.

The gear numbering freely defines as used herein.Also can add creep retaining and/or overgear, in order to for example in vehicle, improve cross-country characteristic or acceleration performance.For example can omit first retaining in addition, in order to for example can optimize transmission gear ratio bulking property at interval preferably.The gear numbering changes by meaning in these measures.

Irrelevant with the corresponding embodiment of dual-clutch transmission, live axle and driven shaft arrange with preferably also differing from one another axle, the layout that structure space is especially saved in this realization.Thereby the axle that sets gradually before and after for example on the space also can stagger each other slightly.In this layout, velocity ratio is that 1 direct retaining can be realized and can relatively freely be placed into the 6th to the 9th in an advantageous manner blocking by the tooth engagement.Also can consider other layout possibility of live axle and driven shaft.

Preferably, the dual-clutch transmission of suggestion is equipped with integrated output stage.This output stage can be included in a fixed gear on the driven shaft as output gear, this fixed gear not only with as first output gear of the fixed gear of first jack shaft and also with second output gear engagement as the fixed gear of second jack shaft.But at least one described output gear can constitute the gear that can connect.

Can handle low forward gear and reverse gear by a startup clutch or shift clutch (Schaltkupplung) by favourable mode, thereby thereby so that with higher load centralization to this clutch and can structure space more save with cost and constitute second clutch more economically.Especially in the dual-clutch transmission of suggestion, each gear plane can be set like this, thereby make and to start by inside or outside transmission input shaft and by the corresponding good clutch that is fit to that this also can realize in the nested configuration mode towards each other in the footpath of the concentric setting of double clutch.In addition, can arrange symmetrically or the change gear plane by corresponding mirror image.

Irrespectively can in dual-clutch transmission, for example exchange the gear plane of setting with corresponding embodiment.Also can replace bidentate wheel plane and use two individual gears planes and/or vice versa.

Description of drawings

Explain the present invention in detail by means of accompanying drawing below.Wherein:

Fig. 1 illustrates the schematic representation by first embodiment of nine retaining dual-clutch transmissions of the present invention;

Fig. 2 illustrates the gearshift figure by first embodiment of Fig. 1;

Fig. 3 illustrates the schematic representation by second embodiment of nine retaining dual-clutch transmissions of the present invention;

Fig. 4 illustrates the gearshift figure by second embodiment of Fig. 3;

Fig. 5 illustrates the schematic representation by the 3rd embodiment of nine retaining dual-clutch transmissions of the present invention;

Fig. 6 illustrates the gearshift figure by the 3rd embodiment of Fig. 5;

Fig. 7 illustrates the schematic representation by the 4th embodiment of nine retaining dual-clutch transmissions of the present invention;

Fig. 8 illustrates the gearshift figure by the 4th embodiment of Fig. 7;

Fig. 9 illustrates the schematic representation by the 5th embodiment of nine retaining dual-clutch transmissions of the present invention;

Figure 10 illustrates the gearshift figure by the 5th embodiment of Fig. 9;

Figure 11 illustrates the schematic representation by the 6th embodiment of nine retaining dual-clutch transmissions of the present invention;

Figure 12 illustrates the gearshift figure by the 6th embodiment of Figure 11;

Figure 13 illustrates the schematic representation by the 7th embodiment of nine retaining dual-clutch transmissions of the present invention;

Figure 14 illustrates the gearshift figure by the 7th embodiment of Figure 13;

Figure 15 illustrates the schematic representation by the 8th embodiment of nine retaining dual-clutch transmissions of the present invention;

Figure 16 illustrates the gearshift figure by the 8th embodiment of Figure 15;

Figure 17 illustrates the schematic representation by the 9th embodiment of nine retaining dual-clutch transmissions of the present invention;

Figure 18 illustrates the gearshift figure by the 9th embodiment of Figure 17;

Figure 19 illustrates the schematic representation by the tenth embodiment of nine retaining dual-clutch transmissions of the present invention;

Figure 20 illustrates the gearshift figure by the tenth embodiment of Figure 19.

Embodiment

The possible embodiment of one nine retaining dual-clutch transmission is shown respectively in Fig. 1,3,5,7,9,11,13,15,17 and 19.Corresponding gearshift figure for each embodiment represents with the form of form in Fig. 2,4,6,8,10,12,14,16,18 and 20.

Nine the retaining dual-clutch transmissions comprises two clutch K1, K2, the input side of described two clutches be connected with a live axle w_an and its outlet side respectively with two coaxially to each other the setting transmission input shaft w_k1, w_k2 in one be connected.In addition, on live axle w_an, torshional vibration damper 22 can be set.Two jack shaft w_v1, w_v2 are set in addition, constitute

free gear

7,8,9,10,11,12,13,14,15,16,17,18 shift gear can be rotated to support on the described jack shaft.That at two transmission input shaft w_k1, w_k2 the rotationally fixedly setting arranged and constitute

fixed gear

1,2,3,4,5,6 shift gear, described shift gear at least part of with

free gear

7,8,9,10,11,12,13,14,15,16,17,18 engagements.

For

free gear

7,8,9,10,11,12,13,14,15,16,17,18 being connected with corresponding jack shaft w_v1, w_v2, a plurality of coupling A, B, C, D, E, F, G, H, I, J, K, L that can activate are arranged on jack shaft w_v1, the w_v2.In addition, be provided as the

output gear

20,21 of constant small gear at two jack shaft w_v1, w_v2, described output gear respectively with the tooth portion engagement of the fixed gear 19 of driven shaft w_ab.

Except coupling A, B, C, D, E, F, G, H, I, J, K, L, at least one also is set in dual-clutch transmission is used for circuitous retaining-switching member M, N that rotationally fixedly connects two shift gears of jack shaft w_v1, a w_v2, in order to realize at least one circuitous retaining, described coupling is implemented in anti-rotational connection the between shift gear and the jack shaft w_v1, the w_v2 that set.

According to the present invention, five gear planes only are set in described dual-clutch transmission, wherein, at least four bidentate wheels plane 7-13,8-14,9-15,10-16,11-17,12-18 are set in each embodiment, make and to connect the circuitous retaining of at least one motility gearshift by at least one switching member M, N that is activated.For example can use claw or analog to connect two gears or analog as switching member M, N respectively.

Press Fig. 1,5,13 and 17 the first, the 3rd, the 7th and the 9th in the embodiment, on the first jack shaft w_v1, switching member M is set respectively so that when switching member M is activated, free gear 9 can be connected with free gear 10.And in pressing Fig. 7,11,15 and 19 the 4th, the 6th, the 8th and the tenth embodiment, switching member N is set respectively on the second jack shaft w_v2, so that when switching member N is activated, free gear 15 can be connected with free gear 16.In pressing the second and the 5th embodiment of Fig. 3 and 9, a switching member M is set respectively on the first jack shaft w_v1, and additionally at the second jack shaft w_v2 another switching member N is set.

In pressing Fig. 1,5,9,17 and 19 the first, the 3rd, the 5th, the 9th and the tenth embodiment, in the first gear plane 8-14 as bidentate wheel plane, the fixed gear 2 of the second transmission input shaft w_k2 respectively not only with the free gear 8 of the first jack shaft w_v1 but also with free gear 14 engagements of the second jack shaft w_v2.In the second gear plane 9-15 as bidentate wheel plane, fixed gear 3 not only with the free gear 9 of the first jack shaft w_v1 but also with free gear 15 engagements of the second jack shaft w_v2.In pressing second embodiment of Fig. 3, in the first gear plane 7-13 as bidentate wheel plane, the fixed gear 1 of the second transmission input shaft w_k2 not only with the free gear 13 of the second jack shaft w_v2 and also with the intermediate gear ZR engagement of countershaft w_zw, this intermediate gear is used for the rotating speed reversing when realizing back gear ratio, wherein, free gear 7 engagements of intermediate gear ZR and the first jack shaft w_v1.Intermediate gear ZR can be rotatably set on the countershaft w_zw, and wherein countershaft w_zw for example is arranged to be parallel to jack shaft w_v1, w_v2.In pressing second embodiment of Fig. 3, in the second gear plane 2-14 as the individual gears plane, the fixed gear 2 of the second transmission input shaft w_k2 only with free gear 14 engagement of the second jack shaft w_v2.

In pressing first embodiment of Fig. 1, in the 3rd gear plane 10-16 as bidentate wheel plane, the fixed gear 4 of the first transmission input shaft w_k1 not only with the free gear 10 of the first jack shaft w_v1 and also with the intermediate gear ZR engagement of countershaft w_zw, this intermediate gear is used for rotating speed and switches to realize back gear ratio.In addition, free gear 16 engagements of intermediate gear ZR and the second jack shaft w_v2.In pressing the 5th embodiment of Fig. 9, the fixed gear 4 of the first transmission input shaft w_k1 and the free gear 16 of the second jack shaft w_v2 and with the intermediate gear ZR of countershaft w_zw engagement.In addition, free gear 10 engagements of intermediate gear ZR and the first jack shaft w_v1.In first embodiment of pressing Fig. 1 with press in the 5th embodiment of Fig. 9, in the 4th gear plane 11-17 as bidentate wheel plane, the fixed gear 5 of the first transmission input shaft w_k1 not only with the free gear 11 of the first jack shaft w_v1 and also with free gear 17 engagements of the second jack shaft w_v2.In above-mentioned two embodiments, in the 5th gear plane 6-18 as the individual gears plane, the fixed gear 6 of the first transmission input shaft w_k1 only with free gear 18 engagement of the second jack shaft w_v2.

In pressing second embodiment of Fig. 3, in the 3rd gear plane 9-15 as bidentate wheel plane, the fixed gear 3 of the second transmission input shaft w_k2 not only with the free gear 9 of the first jack shaft w_v1 and also with free gear 15 engagements of the second jack shaft w_v2.In the 4th gear plane 10-16 as bidentate wheel plane, the fixed gear 4 of the first transmission input shaft w_k1 not only with the free gear 10 of the first jack shaft w_v1 and also with free gear 16 engagements of the second jack shaft w_v2.At last, in the 5th gear plane 11-17 as bidentate wheel plane, the fixed gear 5 of the first transmission input shaft w_k1 not only with the free gear 11 of the first jack shaft w_v1 and also with free gear 17 engagements of the second jack shaft w_v2.

In addition, in pressing the 9th embodiment of Figure 17, in the 3rd gear plane 10-16 as bidentate wheel plane, the fixed gear 4 of the first transmission input shaft w_k1 not only with the free gear 10 of the first jack shaft w_v1 and also with the intermediate gear ZR engagement of countershaft w_zw, wherein, intermediate gear ZR again with free gear 16 engagement of the second jack shaft w_v2.In the 4th gear plane 11-17 as bidentate wheel plane, the fixed gear 5 of the first transmission input shaft w_k1 not only with the free gear 11 of the first jack shaft w_v1 and also with free gear 17 engagements of the second jack shaft w_v2.At last, in the 5th gear plane 12-18 as bidentate wheel plane, the fixed gear 6 of the first transmission input shaft w_k1 not only with the free gear 12 of the first jack shaft w_v1 and also with free gear 18 engagements of the second jack shaft w_v2.Different with the 9th embodiment is, in the tenth embodiment, the intermediate gear ZR that is used for the rotating speed reversing is arranged on the 5th midplane 12-18, thereby in pressing the tenth embodiment of Figure 19, the fixed gear 6 of intermediate gear ZR and transmission input shaft w_k1 and 18 engagements of the free gear of the second jack shaft w_v2.

In pressing the 3rd embodiment of Fig. 5, in the 3rd gear plane 10-4 as the individual gears plane, the fixed gear 4 of the first transmission input shaft w_k1 only with free gear 10 engagement of the first jack shaft w_v1.In the 4th gear plane 11-17 as bidentate wheel plane, the fixed gear 5 of the first transmission input shaft w_k1 not only with the free gear 11 of the first jack shaft w_v1 and also with free gear 17 engagements of the second jack shaft w_v2.At last, in the 5th gear plane 12-18 as bidentate wheel plane, the fixed gear 6 of the first transmission input shaft w_k1 not only meshes with the free gear 18 of the second jack shaft w_v2 but also with intermediate gear ZR countershaft w_zw, that be used for the rotating speed reversing.Free gear 12 engagements of intermediate gear ZR and the first jack shaft w_v1.

In pressing the 4th and the 6th embodiment of Fig. 7 and 11, in the first gear plane 1-13 or 7-1 as the individual gears plane, the fixed gear 1 of the second transmission input shaft w_k2 and the free gear 13 of the second jack shaft w_v2 otherwise with free gear 7 engagements of the first jack shaft w_v1.In above-mentioned two embodiments, in the second gear plane 8-14 as bidentate wheel plane, the fixed gear 2 of second transmission input shaft not only with the free gear 14 of the second jack shaft w_v2 and also with the intermediate gear ZR engagement of countershaft w_zw, this intermediate gear is used for the rotating speed reversing of back gear ratio.Intermediate gear ZR again with free gear 8 engagement of the first jack shaft w_v1.In the 3rd gear plane 9-15 as bidentate wheel plane, the fixed gear 3 of the second transmission input shaft w_k2 not only with the free gear 9 of first jack shaft and also with free gear 15 engagements of the second jack shaft w_v2.

Press Figure 13 and 15 in the 7th and the 8th embodiment, in the first gear plane 7-13 as bidentate wheel plane, the fixed gear 1 of the second transmission input shaft w_k2 not only with the free gear 7 of the first jack shaft w_v1 and also with free gear 13 engagements of the second jack shaft w_v2.In the second gear plane 8-14 as bidentate wheel plane, the fixed gear 2 of the second transmission input shaft w_k2 not only with the free gear 8 of the first jack shaft w_v1 and also with free gear 14 engagements of the second jack shaft w_v2.In the 7th embodiment, in the 3rd gear plane 9-15 as bidentate wheel plane, the fixed gear 3 of the second transmission input shaft w_k2 not only with the free gear 9 of the first jack shaft w_v1 and also with the intermediate gear ZR engagement of countershaft w_zw, wherein, intermediate gear ZR again with free gear 15 engagement of the second jack shaft w_v2.In the 8th embodiment, the free gear 15 of fixed gear 3 and the second jack shaft w_v2 and the intermediate gear ZR of countershaft w_zw engagement, wherein intermediate gear ZR again with free gear 9 engagements of the first jack shaft w_v1.

In pressing Fig. 7,11,13 and 15 the 4th, the 6th, the 7th and the 8th embodiment, in the 4th gear plane 10-16 as bidentate wheel plane, the fixed gear 4 of the first transmission input shaft w_k1 not only with the free gear 10 of the first jack shaft w_v1 and also with free gear 16 engagements of the second jack shaft w_v2.In the 5th gear plane 11-17 as bidentate wheel plane, the fixed gear 5 of the first transmission input shaft w_k1 not only with the free gear 11 of the first jack shaft w_v1 and also with free gear 17 engagements of the second jack shaft w_v2.

According to pressing Fig. 1,5,9,17 and 19 the first, the 3rd, the 5th, the 9th and the tenth embodiment, not only on the first jack shaft w_v1 but also at coupling B-C or H-I that two-sided action is set respectively between the first gear plane 8-14 and the second gear plane 9-15 on the second jack shaft w_v2.When corresponding coupling B or C are activated, on the first jack shaft w_v1, make free gear 8 and by coupling C free gear 9 is fixedlyed connected with the first jack shaft w_v1 by coupling B.When coupling H or coupling I are activated, on the second jack shaft w_v2, make free gear 14 and by coupling I free gear 15 is fixedlyed connected with the second jack shaft w_v2 by coupling H.

In addition, in pressing first embodiment of Fig. 1, between the 3rd gear plane 10-16 and the 4th gear plane 11-17 not only on the first jack shaft w_v1 but also coupling device D-E or the J-K of a two-sided action be set respectively on the second jack shaft w_v2.When coupling D or E were activated, free gear 10 was by coupling D and free gear 11 is fixedlyed connected with the first jack shaft w_v1 by coupling E on the first jack shaft w_v1.When coupling J or K were activated, free gear 16 was by coupling J and free gear 17 is fixedlyed connected with the second jack shaft w_v2 by coupling K on the second jack shaft w_v2.In addition, in pressing first embodiment of Fig. 1, at the second jack shaft w_v2 a single coupling L is set between the 4th gear plane 11-17 and the 5th gear plane 6-18, this coupling is fixedlyed connected free gear 18 under the state that is activated with the second jack shaft w_v2.

In pressing the 3rd and the tenth embodiment of Fig. 5 and 19, between the 3rd gear plane 10-4 or 10-16 and the 4th gear plane 11-17, the first jack shaft w_v1 is equipped with the coupling D-E of a two-sided action, and the second jack shaft w_v2 is equipped with the coupling K of an one-sided effect.Coupling D is fixedlyed connected free gear 10 with the first jack shaft w_v1, and coupling E is fixedlyed connected free gear 11 with the first jack shaft w_v1, and wherein coupling K is fixedlyed connected free gear 17 under the state that is activated with the second jack shaft w_v2.In addition, in the 3rd and the tenth embodiment, between the 4th gear plane 11-17 and the 5th gear plane 12-18, the first jack shaft w_v1 is equipped with the coupling F of an one-sided effect, and the second jack shaft w_v2 is equipped with the coupling L of an one-sided effect.Coupling F can be fixedlyed connected free gear 12 under the state that is activated with the first jack shaft w_v1, and coupling L can be fixedlyed connected free gear 18 under the state that is activated with the second jack shaft w_v2.

In pressing the 5th and the 9th embodiment of Fig. 9 and 17, between the 3rd gear plane 10-16 and the 4th gear plane 11-17, the first jack shaft w_v1 is equipped with the coupling E of an one-sided effect, and the second jack shaft w_v2 is equipped with the coupling J-K of a two-sided action.Coupling E is fixedlyed connected free gear 11 under the state that is activated with the first jack shaft w_v1.Coupling J is fixedlyed connected free gear 16 under the state that is activated with the second jack shaft w_v2.Coupling K is fixedlyed connected free gear 17 under the state that is activated with the second jack shaft w_v2.In addition, between the 4th gear plane 11-17 and the 5th gear plane 6-18 or 12-18, at the second jack shaft w_v2 coupling L of an one-sided effect is set, in order under the state that is activated, free gear 18 is fixedlyed connected with the second jack shaft w_v2.In addition, in pressing the 9th embodiment of Figure 17, at the first jack shaft w_v1 coupling F of an one-sided effect is set, in order under the state that is activated, free gear 12 is fixedlyed connected with the first jack shaft w_v1.

In the second, the 7th and the 8th embodiment, the first jack shaft w_v1 and the second jack shaft w_v2 set coupling A and the G of an one-sided effect respectively between the first face of gear 7-13 and the second face of gear 8-14 or 2-14 according to Fig. 3,13 and 15.Coupling A can be fixedlyed connected free gear 7 under the state that is activated with the first jack shaft w_v1, and coupling G can be fixedlyed connected free gear 13 under the state that is activated with the second jack shaft w_v2.

In pressing the 4th embodiment of Fig. 7, between the first gear plane 1-13 and the second gear plane 8-14, only the second jack shaft w_v2 is equipped with the coupling G of an one-sided effect, wherein, this coupling is fixedlyed connected free gear 13 under the state that is activated with the second jack shaft w_v2.In the 6th embodiment of Figure 11, between the first gear plane 7-1 and the second gear plane 8-14, only the first jack shaft w_v1 is equipped with the coupling A of an one-sided effect, and this coupling is fixedlyed connected free gear 7 under the state that is activated with the first jack shaft w_v1.In addition, in these two embodiments, between the second gear plane 8-14 and the 3rd gear plane 9-15, the first jack shaft w_v1 or the second jack shaft w_v2 are equipped with coupling B-C or the H-I of each two-sided action, wherein, coupling B is fixedlyed connected free gear 8 with the first jack shaft w_v1, and coupling C is fixedlyed connected free gear 9 with the first jack shaft w_v1, and coupling H fixedlys connected free gear 14 with the second jack shaft w_v2, and coupling I is fixedlyed connected free gear 15 with the second jack shaft w_v2.

In pressing the second and the 7th embodiment of Fig. 3 and 13, between the second gear plane 2-14 or 8-14 and the 3rd gear plane 9-15, the first jack shaft w_v1 is equipped with coupling C or the B of an one-sided effect, and the second jack shaft w_v2 is equipped with the coupling H-I of a two-sided action.Coupling C is fixedlyed connected free gear 9 under the state that is activated with the first jack shaft w_v1, and coupling B is fixedlyed connected free gear 8 with the first jack shaft w_v1.Coupling H is fixedlyed connected free gear 14 under the state that is activated with the second jack shaft w_v2, and coupling I is fixedlyed connected free gear 15 under the state that is activated with the second jack shaft w_v2.

In the 8th embodiment, between the second gear plane 8-14 and the 3rd gear plane 9-15, the first jack shaft w_v1 is equipped with the coupling B-C of a two-sided action according to Figure 15, and second jack shaft is equipped with the coupling H of an one-sided effect.Coupling B is fixedlyed connected free gear 8 under the state that is activated with the first jack shaft w_v1, and coupling C is fixedlyed connected free gear 9 under the state that is activated with the first jack shaft w_v1.Coupling H is fixedlyed connected free gear 14 under the state that is activated with the second jack shaft w_v2.

In pressing Fig. 3,7,11,13 and 15 the second, the 4th, the 6th, the 7th and the 8th embodiment, between the 4th gear plane 10-16 and gear plane 11-17, first jack shaft and second jack shaft set coupling D-E or the J-K of a two-sided action respectively.Coupling D is fixedlyed connected free gear 10 under the state that is activated with the first jack shaft w_v1, and coupling E is fixedlyed connected free gear 11 under the state that is activated with the first jack shaft w_v1.Coupling J is fixedlyed connected free gear 16 under the state that is activated with the second jack shaft w_v2, and coupling K is fixedlyed connected free gear 17 under the state that is activated with the second jack shaft w_v2.

In according to dual-clutch transmission of the present invention, an integrated output stage can be provided with the output gear 20 that is connected with the first jack shaft w_v1 rotationally fixedly and be arranged on output gear 21 on the second jack shaft w_v2.Output gear 20 and output gear 21 respectively with fixed gear 19 engagement of driven shaft w_ab.But also possiblely be,

output gear

20 or 21 with the jack shaft w_v1 that sets or w_v2 between realize can break-make be connected.

Irrelevant with each embodiment, in according to dual-clutch transmission of the present invention, obtain, forward gear G1 to G9 is that motility gearshift ground can be carried out at least.

By the gearshift figure according to first embodiment of the nine retaining dual-clutch transmissions of Fig. 1 of form example shown shown in figure 2.

Figure obtains by this gearshift, the first forward gear G1 can be by first clutch K1 and coupling I and the switching member M connection by being activated by being activated as circuitous retaining, the second forward gear G2 can connect by second clutch K2 with by the coupling I that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling D that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling C that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling K that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling H that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling E that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling B that is activated, and the 9th forward gear G9 can carry out by first clutch K1 with by the coupling L that is activated.

In the first embodiment, also obtained by form shown in Figure 2, the R1 that reverses gear can connect by first clutch K1 with by the coupling J that is activated.In addition, in by dual-clutch transmission first embodiment, that advise, overgear O1 as circuitous retaining can be by second clutch K2, connect by the coupling L that is activated with by the switching member M that is activated.In an advantageous manner can be between overgear O1 and the 9th forward gear G9 under load, be gearshift interruptedly of tractive force.

By form example shown shown in Figure 4 gearshift figure according to second embodiment of the nine retaining dual-clutch transmissions of Fig. 3.

Figure obtains by this gearshift, the first forward gear G1 can be by first clutch K1 and coupling G and the switching member M connection by being activated by being activated as circuitous retaining, the second forward gear G2 can connect by second clutch K2 with by the coupling G that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling J that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling H that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling D that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling I that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling K that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling C that is activated, and the 9th forward gear G9 can carry out by first clutch K1 with by the coupling E that is activated.

Also obtained by form shown in Figure 4 in second embodiment, the R1 that reverses gear can be by first clutch K1 and coupling A and the switching member N connection by being activated by being activated as circuitous retaining.In addition, the retaining C1 that creeps can be by first clutch K1 and coupling G and the switching member N connection by being activated by being activated as circuitous retaining.

In addition, in dual-clutch transmission that advise, by second embodiment, overgear O1 as circuitous retaining can be by second clutch K2, connect by the coupling E that is activated and by the switching member M that is activated.Can between overgear O1 and the 9th forward gear G9, carry out power gear shifting in an advantageous manner.In addition, can alternatively or additionally set, another overgear O2 passes through second clutch K2 as circuitous retaining, by coupling K and the switching member M connection by being activated that is activated, next overgear O3 passes through second clutch K2 as circuitous retaining, by coupling E and the switching member N connection by being activated that is activated, same motility of O3 the 9th forward gear G9 ground of shifting gears in this overgear is carried out, another overgear O4 passes through second clutch K2 as circuitous retaining, by coupling D and the switching member N connection by being activated that is activated, and next overgear O5 passes through second clutch K2 as circuitous retaining, by coupling K and the switching member N connection by being activated that is activated.

By form example shown shown in Figure 6 gearshift figure according to the 3rd embodiment of the nine retaining dual-clutch transmissions of Fig. 5.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling E that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling B that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling K that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling H that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling L that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling C that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling D that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling I that is activated, and the 9th forward gear G9 can carry out by first clutch K1 with by the coupling I that is activated and the switching member M that passes through to activate as circuitous retaining.

Also obtained by form shown in Figure 6 in the 3rd embodiment, the R1 that reverses gear can be by second clutch K2 and coupling F and the switching member M connection by being activated by being activated as circuitous retaining.

By form example shown shown in Figure 8 gearshift figure according to the 4th embodiment of the nine retaining dual-clutch transmissions of Fig. 7.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling E that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling H that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling K that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling C that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling D that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling I that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling J that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling G that is activated, and the 9th forward gear G9 can be by first clutch K1 and coupling G and the switching member N execution by being activated by being activated as circuitous retaining.

In the 4th embodiment, also obtained by form shown in Figure 8, the R1 that reverses gear can connect by second clutch K2 with by the coupling B that is activated, and/or another R2 that reverses gear can be by first clutch K1 and coupling B and the switching member N connection by being activated by being activated as circuitous retaining.Reverse gear R1 and R2 is mutual power gear shifting in an advantageous manner.In addition, the circuitous retaining of retaining C1 conduct of creeping can be by second clutch K2 and coupling E and the switching member N connection by being activated by being activated, and wherein creep retaining C1 and the first forward gear G1 are can mutual power gear shifting.

In addition, in the dual-clutch transmission of advising according to the 4th embodiment, overgear O1 as circuitous retaining can be by first clutch K1, connect by the coupling G that is activated and by the switching member M that is activated.

By form example shown shown in Figure 10 gearshift figure according to the 5th embodiment of the nine retaining dual-clutch transmissions of Fig. 9.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling L that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling H that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling K that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling B that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling E that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling I that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling J that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling C that is activated, and the 9th forward gear G9 can be by first clutch K1 and coupling C and the switching member N execution by being activated by being activated as circuitous retaining.

In the 5th embodiment, also obtained by form shown in Figure 10, the R1 that reverses gear can be by second clutch K2 and coupling L and the switching member M connection by being activated by being activated as circuitous retaining.Therefore, reverse gear R1 and the first forward gear G1 is mutual power gear shifting.In addition, the retaining C1 that creeps can be by second clutch K2 and coupling L and the switching member N connection by being activated by being activated as circuitous retaining.Creep retaining C1 and the first forward gear G1 also be can mutual power gear shifting (C1 lsb. is to G1).

For example represented to keep off the gearshift figure of the 6th embodiment of dual-clutch transmissions according to nine of Figure 11 by form shown in Figure 12.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling E that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling H that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling K that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling C that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling D that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling I that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling J that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling A that is activated, and the 9th forward gear G9 can be by first clutch K1 and coupling A and the switching member N execution by being activated by being activated as circuitous retaining.

In the 6th embodiment, also obtained by form shown in Figure 12, R1 that reverses gear (R1 motility shift gears G1) can connect by second clutch K2 with by the coupling B that is activated, and/or another R2 that reverses gear (R2 motility shift gears R1) can connect by first clutch K1 with by the coupling B that is activated and by the switching member N that is activated as circuitous retaining.In addition, the retaining C1 that creeps can carry out (C1 motility shift gears G1) by second clutch K2 with by the coupling E that is activated and by the switching member M that is activated as circuitous retaining.Alternatively or additionally, another retaining C2 that creeps (C2 motility shift gears G1) can connect by second clutch K2 with by the coupling E that is activated and by the switching member N motility gearshift ground (lsb.) that is activated as circuitous retaining.

For example represented to keep off the gearshift figure of the 7th embodiment of dual-clutch transmissions according to nine of Figure 13 by form shown in Figure 14.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling J that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling H that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling D that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling B that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling K that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling G that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling E that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling A that is activated, and the 9th forward gear G9 can be by first clutch K1 and coupling A and the switching member M execution by being activated by being activated as circuitous retaining.

In the 7th embodiment, also obtained by form shown in Figure 14, the R1 that reverses gear can connect by first clutch K1 with by the coupling I that is activated and by the switching member M that is activated as circuitous retaining, and/or another R2 that reverses gear can connect by first clutch K1 with by the coupling H that is activated and by the switching member N that is activated as circuitous retaining.

For example represented to keep off the gearshift figure of the 8th embodiment of dual-clutch transmissions according to nine of Figure 15 by form shown in Figure 16.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling J that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling H that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling D that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling B that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling K that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling G that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling E that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling A that is activated, and the 9th forward gear G9 can carry out by first clutch K1 with by the coupling A that is activated and the switching member N that is activated as circuitous retaining.

In the 8th embodiment, also obtained by form shown in Figure 16, R1 that reverses gear (R1 motility shift gears G1) can connect by second clutch K2 with by the coupling C that is activated, and/or the next R2 that reverses gear can carry out (R2 motility shift gears G1) by second clutch K2 with by the coupling J that is activated and by the switching member M that is activated as circuitous retaining, and/or another R3 that reverses gear can carry out by first clutch K1 with by the coupling I that is activated and by the switching member M that is activated as circuitous retaining, and/or the next one R4 that reverses gear can carry out by first clutch K1 with by the coupling C that is activated and by the switching member N that is activated as circuitous retaining (R4 motility shift gears R1).

For example represented to keep off the gearshift figure of the 9th embodiment of dual-clutch transmissions according to nine of Figure 17 by form shown in Figure 18.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling L that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling I that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling F that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling C that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling K that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling H that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling E that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling B that is activated, and the 9th forward gear G9 can be by first clutch K1 and coupling B and the switching member M execution by being activated by being activated as circuitous retaining.

In the 9th embodiment, by also drawing at the form shown in Figure 18, the R1 that reverses gear can connect by second clutch K2 with by the coupling J that is activated and by the switching member M that activates as circuitous retaining, and/or another R2 that reverses gear (R2 motility shift gears G1) can connect by second clutch K2 and the coupling that is activated L and by the switching member N that is activated as circuitous retaining.In addition, the retaining C1 (C1 motility shift gears G1) that creeps can connect by second clutch K2 with by the coupling L that is activated and by the switching member M that is activated as circuitous retaining.

For example represented to keep off the gearshift figure of the tenth embodiment of dual-clutch transmissions according to nine of Figure 19 by form shown in Figure 20.

Figure obtains by this gearshift, the first forward gear G1 can connect by first clutch K1 with by the coupling K that is activated, the second forward gear G2 can connect by second clutch K2 with by the coupling I that is activated, the 3rd forward gear G3 can connect by first clutch K1 with by the coupling E that is activated, the 4th forward gear G4 can connect by second clutch K2 with by the coupling C that is activated, the 5th forward gear G5 can connect by first clutch K1 with by the coupling D that is activated, the 6th forward gear G6 can connect by second clutch K2 with by the coupling H that is activated, the 7th forward gear G7 can connect by first clutch K1 with by the coupling F that is activated, the 8th forward gear G8 can connect by second clutch K2 with by the coupling B that is activated, and the 9th forward gear G9 can be by first clutch K1 and coupling B and the switching member N execution by being activated by being activated as circuitous retaining.

In the tenth embodiment, also obtained by form shown in Figure 20, the R1 that reverses gear can connect as circuitous retaining by second clutch K2 with by the coupling L that is activated and by the switching member M that is activated by first clutch K1 with by the coupling L that is activated and/or another R2 that reverses gear (R2 motility shift gears R1), and/or the next one R3 (R3 motility shift gears R1) that reverses gear can connect as circuitous retaining by second clutch K2 with by the coupling L that is activated and by the switching member N that is activated.In addition, the retaining C1 (C1 motility shift gears G1) that creeps can connect by second clutch K2 with by the coupling K that is activated and by the switching member M that is activated as circuitous retaining.In addition, alternatively or additionally, another retaining C2 that creeps (C2 motility shift gears G1) can connect by second clutch K2 with by the coupling K that is activated and by the switching member N that is activated as circuitous retaining.In addition, an overgear O1 can be by first clutch K1 and coupling B and the switching member M connection by being activated by being activated as circuitous retaining.

At length obtained by the gearshift figure by Fig. 2, use gear stage i_3, i_4 and i_2 from first clutch K1 in the first forward gear G1, wherein these two speed changer parts are coupled by switching member M in the first embodiment.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, in the 8th forward gear G8, use gear stage i_8 and in the 9th forward gear G9, use gear stage i_9.In addition, in the R1 that reverses gear, use gear stage i_R.Use gear stage i_4, i_3 and i_9 from second clutch K2 in the O1 of overgear, wherein these two speed changer parts are coupled by switching member M.

At length obtained by the gearshift figure by Fig. 4, use gear stage i_5, i_8 and i_2 from first clutch K1 in the first forward gear G1, wherein these two speed changer parts are coupled by switching member M in second embodiment.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, in the 8th forward gear G8, use gear stage i_8 and in the 9th forward gear G9, use gear stage i_9.In addition, use gear stage i_3, i_6 and i_R from first clutch K1 in the R1 that reverses gear, wherein these two speed changer parts are coupled by switching member N.Use gear stage i_3, i_6 and i_2 from first clutch K1 in the retaining C1 that creeps, wherein these two speed changer parts are coupled by switching member N.Use gear stage i_8, i_5 and i_9 from second clutch K2 in the O1 of overgear, wherein these two speed changer parts are coupled by switching member M.Use gear stage i_8, i_5 and i_7 from second clutch K2 in the O2 of another overgear, wherein these two speed changer parts are coupled by switching member M.In the O3 of overgear, use gear stage i_6, i_3 and i_9 from second clutch K2.In the O4 of overgear, use gear stage i_6, i_3 and i_5 from second clutch K2.In the O5 of overgear, use gear stage i_6, i_3 and i_7 from second clutch K2 at last.In the O3 to O5 of overgear, use switching member N to be coupled two speed changer parts respectively.

At length obtained by the gearshift figure by Fig. 6, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage i_7, i_6 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member M.In addition, use gear stage i_6, i_7 and i_R from second clutch K2 in the R1 that reverses gear, wherein these two speed changer parts are coupled by switching member M.

At length obtained by the gearshift figure by Fig. 8, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage i_7, i_6 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member N.In addition, in the R1 that reverses gear, use gear stage i_R.Use gear stage i_7, i_6 and i_R from first clutch K1 in another reverses gear R2, wherein these two speed changer parts are coupled by switching member N.Use gear stage i_6, i_7 and i_1 from second clutch K2 in the retaining C1 that creeps, wherein these two speed changer parts are coupled mutually by switching member N.At last, use gear stage i_5, i_4 and i_8 from first clutch K1 in the O1 of overgear, wherein these two speed changer parts are coupled mutually by switching member M.

At length obtained by the gearshift figure by Figure 10, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage i_7, i_6 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member N.In addition, use gear stage i_8, i_R and i_1 from second clutch K2 in the R1 that reverses gear, wherein these two speed changer parts are coupled by switching member M.Use gear stage i_6, i_7 and i_1 from second clutch K2 in the retaining C1 that creeps, wherein these two speed changer parts are coupled mutually by switching member N.

Different with the gearshift figure that presses Figure 10, in by the gearshift figure of Figure 12, use gear stage i_R at the R1 that reverses gear, and use gear stage i_7, i_6 and i-R at another R2 that reverses gear from first clutch K1, wherein switching member N is used for being coupled two speed changer parts.Another difference is, in the retaining C1 that creeps, use gear stage i_4, i_5 and i_1 from second clutch K2, wherein these two speed changer parts are coupled by switching member M, and use gear stage i_6, i_7 and i_1 from second clutch K2 in the retaining C2 that creeps, wherein these two speed changer parts are coupled by switching member N.

At length obtained by the gearshift figure by Figure 14, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage i_3, zw_9 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member M.In addition, use gear stage i_3, zw_9 and i_R from first clutch K1 in the R1 that reverses gear, wherein these two speed changer parts are coupled by switching member M.Use gear stage i_1, i_R and i_2 from first clutch K1 in the R2 that reverses gear, wherein these two speed changer parts are coupled mutually by switching member N.

At length obtained by the gearshift figure by Figure 16, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage i_1, zw_9 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member N.In addition, in the R1 that reverses gear, use gear stage i_R.Use gear stage i_R, i_3 and i_1 from second clutch K2 in the R2 that reverses gear, wherein these two speed changer parts are coupled by switching member M.Use gear stage i_3, i_R and zw_9 from first clutch K1 in the R3 that reverses gear, wherein these two speed changer parts are coupled mutually by switching member M.At last, use gear stage i_1, zw_9 and i_R from first clutch K1 in the R4 that reverses gear, wherein these two speed changer parts are coupled mutually by switching member N.

At length obtained by the gearshift figure by Figure 18, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage zw_9, i_4 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member M.In addition, use gear stage i_4, zw_9 and i_R from second clutch K2 in the R1 that reverses gear, wherein these two speed changer parts are coupled by switching member M.Use gear stage i_2, i_R and i_1 from second clutch K2 in the R2 that reverses gear, wherein these two speed changer parts are coupled mutually by switching member N.At last, use gear stage i_4, zw_9 and i_1 from second clutch K2 in the retaining C1 that creeps, wherein these two speed changer parts are coupled mutually by switching member M.

At length obtained by the gearshift figure by Figure 20, in the first forward gear G1, use gear stage i_1.In addition, in the second forward gear G2, use gear stage i_2, in the 3rd forward gear G3, use gear stage i_3, in the 4th forward gear G4, use gear stage i_4, in the 5th forward gear G5, use gear stage i_5, in the 6th forward gear G6, use gear stage i_6, in the 7th forward gear G7, use gear stage i_7, use gear stage i_8 and use gear stage zw_9, i_2 and i_8 from first clutch K1 in the 8th forward gear G8 in the 9th forward gear G9, wherein these two speed changer parts are coupled by switching member N.In addition, in the R1 that reverses gear, use gear stage i_R.Use gear stage i_4, i_5 and i_R from second clutch K2 in the R2 that reverses gear, wherein these two speed changer parts are coupled by switching member M.Use gear stage i_2, zw_9 and i_R from second clutch K2 in the R3 that reverses gear, wherein these two speed changer parts are coupled mutually by switching member N.In the retaining C1 that creeps, use gear stage i_4, i_5 and i_1 from second clutch K2, wherein these two speed changer parts are coupled mutually by switching member M, and use gear stage i_2, zw_9 and i_1 from second clutch K2 in the retaining C2 that creeps, wherein these two speed changer parts are coupled mutually by switching member N.Use gear stage i_5, i_4 and i_8 from first clutch K1 at last in the O1 of overgear, wherein these two speed changer parts are coupled mutually by switching member M.

In pressing first embodiment of Fig. 1 and 2, need especially little structure space owing to save member in a word, because only need a switching member to carry out circuitous retaining.In addition, four bidentate wheel planes and an individual gears plane are set in the first embodiment, wherein the first forward gear G1 connects by the gear stage of the 3rd, the 4th and second forward gear as circuitous retaining.In addition, the shift gears overgear O1 of the 9th forward gear of motility for example can be used as the tenth forward gear.This causes conservation of fuel in an advantageous manner.

At length obtain in the first embodiment, on the first gear plane 8-14 as bidentate wheel plane, free gear 8 is used for a forward gear G8, and wherein free gear 14 is same for a forward gear G6.On the second gear plane 9-15 as bidentate wheel plane, free gear 9 is used for three forward gear G1, G4 and O1, and wherein free gear 15 is used for two forward gear G1 and G2.On the 3rd gear plane 10-16 as bidentate wheel plane, free gear 10 is used for three forward gear G1, G3 and O1, and free gear 16 is used for the R1 that reverses gear.On the 4th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G7, and free gear 17 is same for a forward gear G5.At last, on the 5th gear plane 6-18 as the individual gears plane, free gear 18 is used for two forward gear G9 and O1.

In a word, obtain in second embodiment by Fig. 3 and 4, first forward gear is realized by the velocity ratio of the 5th, the 8th and second forward gear as circuitous retaining.In addition, four bidentate wheel planes and an individual gears plane only are set, they comprise two circuitous retaining-switching member M, N.In addition, the shift gears retaining C1 that creeps of the second forward gear G2 of motility is possible, has improved the rideability when cross-country thus.In addition, the corresponding motility that obtains adding is shifted gears overgear O1, the O3 of the 9th forward gear G9 as the tenth possible forward gear, and this causes conservation of fuel.

At length obtain in second embodiment, on the first gear plane 7-13 as bidentate wheel plane, free gear 7 is used for the R1 that reverses gear, and free gear 13 is used for three forward gear G1, G2, C1.On the second gear plane 2-14 as the individual gears plane, free gear 14 is used for a forward gear G4.On the 3rd gear plane 9-15 as bidentate wheel plane, free gear 9 is used for four forward gear G1, G8, O1 and O2, and free gear 15 is used for five forward G6, C1, O3, O4, O5 and is used for the R1 that reverses gear.On the 4th gear plane 10-16 as bidentate wheel plane, free gear 10 is used for five forward G1, G5, O1, O2, O4, and free gear 16 is used for five forward G3, C1, O3, O4, O5 and is used for the R1 that reverses gear.At last, on the 5th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for three forward gear G9, O1, O3, and free gear 17 is used for three forward gear G7, O2, O5.

In a word, obtain in the 3rd embodiment by Fig. 5 and 6, the 9th forward gear G9 of motility gearshift passes through the gear stage of the 7th, the 6th and the 8th forward gear so that only realize on four bidentate wheel planes and an individual gears plane as circuitous retaining.In addition, only need a circuitous retaining-switching member M to realize circuitous retaining, this causes the advantage on the structure space.In addition, second clutch K2 can be specified to less size owing to less load, because the first forward gear G1 and the 3rd forward gear G3 and the R1 that reverses gear connect by first clutch K1.

At length obtain in the 3rd embodiment, on the first gear plane 8-14 as bidentate wheel plane, free gear 8 is used for a forward gear G2, and free gear 14 is used for a forward gear G4.On the second gear plane 9-15 as bidentate wheel plane, free gear 9 is used for two forward gear G6, G9 and the R1 that reverses gear, and free gear 15 is used for two forward gear G8, G9.On the 3rd gear plane 10-4 as the individual gears plane, free gear 10 is used for two forward gear G7, G9 and is used for the R1 that reverses gear.On the 4th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G1, and free gear 17 is used for a forward gear G3.At last, on the 5th gear plane 12-18 as bidentate wheel plane, free gear 12 is used for the R1 that reverses gear, and free gear 18 is used for a forward gear G5.

In a word, obtain in the 4th embodiment by Fig. 7 and 8, the 9th forward gear G9 of motility gearshift realizes with four bidentate wheel planes and an individual gears plane by the gear stage of the 7th, the 6th and the 8th forward gear as circuitous retaining.Only need a circuitous retaining-switching member N to realize circuitous retaining in addition, this causes the advantage on the structure space.In addition, the shift gears retaining C1 that creeps of the first forward gear G1 of motility can be used as possible the tenth forward gear and realizes, has improved the ride characteristic when cross-country thus.Can realize conservation of fuel by overgear O1 additional, that motility is shifted gears the 8th forward gear G8.

At length obtain in the 4th embodiment, on the first gear plane 1-13 as the individual gears plane, free gear 13 is used for three forward gear G8, G9, O1.On the second gear plane 8-14 as bidentate wheel plane, free gear 8 is used for two R1 that reverse gear, R2, and free gear 14 is used for a forward gear G2.On the 3rd gear plane 9-15 as bidentate wheel plane, free gear 9 is used for two forward gear G4, O1, and free gear 15 is used for three forward gear G6, G9, C1 and the R2 that reverse gear.On the 4th gear plane 10-16 as bidentate wheel plane, free gear 10 is used for two forward gear G5, O1, and free gear 16 is used for three forward gear G7, G9, C1 and is used for the R2 that reverses gear.At last, on the 5th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for two forward gear G1, C1, and free gear 17 is used for a forward gear G3.

In a word, obtain in the 5th embodiment by Fig. 9 and 10, the 9th forward gear G9 of motility gearshift realizes with four bidentate wheel planes and an individual gears plane by the gear stage of the 7th, the 6th and the 8th forward gear as circuitous retaining.Need two circuitous retaining-switching member M, N to realize circuitous retaining.In addition, can realize shift gears the reverse gear R1 of retaining C1 as the tenth possible forward gear and the gearshift of motility that creep of the first forward gear G1 of a motility.Therefore, by the first forward gear G1 and the conversion between the R1 of reversing gear, freely advance and retreat (Freischaukeln) is possible.Obtain better transition between the use of vehicle street and cross-country use generally.

At length obtain in the 5th embodiment, on the first gear plane 8-14 as bidentate wheel plane, free gear 8 is used for a forward gear G4, and free gear 14 is same for a forward gear G2.On the second gear plane 9-15 as bidentate wheel plane, free gear 9 is used for two forward gear G8, G9 and the R1 that reverses gear, and free gear 15 is used for three forward gear G6, G9, C1.On the 3rd gear plane 10-16 as bidentate wheel plane, free gear 10 is used for the R1 that reverses gear, and free gear 16 is used for three forward gear G7, G9, C1.On the 4th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G5, and free gear 17 is used for a forward gear G3.At last, on the 5th gear plane 6-18 as the individual gears plane, free gear 18 is used for two forward gear G1, C1 and is used for the R1 that reverses gear.

In a word, obtain in the 6th embodiment by Figure 11 and 12, the 9th forward gear G9 of motility gearshift realizes with four bidentate wheel planes and an individual gears plane by the gear stage of the 7th, the 6th and the 8th forward gear as circuitous retaining.Only need a circuitous retaining-switching member N to realize circuitous retaining in addition, this causes the advantage on the structure space.In addition, shift gears creep retaining C1, the C2 of the first forward gear G1 of two motilities can realize as the tenth possible forward gear, improves the ride characteristic when cross-country thus.

At length obtain in the 6th embodiment, on the first gear plane 7-1 as the individual gears plane, free gear 7 is used for two forward gear G8, G9.On the second gear plane 8-14 as bidentate wheel plane, free gear 8 is used for two R1 that reverse gear, R2, and free gear 14 is used for a forward gear G2.On the 3rd gear plane 9-15 as bidentate wheel plane, free gear 9 is used for two forward gear G4, C1, and free gear 15 is used for three forward gear G6, G9, C2 and the R2 that reverse gear.On the 4th gear plane 10-16 as bidentate wheel plane, free gear 10 is used for two forward gear G5, C1, and free gear 16 is used for three forward gear G7, G9, C2 and the R2 that reverse gear.At last, on the 5th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for three forward gear G1, C1, C2, and free gear 17 is used for a forward gear G3.

In a word, in the 7th, the 8th, the 9th and the tenth embodiment by Figure 13 to 20, obtain, the 9th forward gear of motility gearshift is the circuitous retaining of motility gearshift, wherein, be provided with five bidentate wheel planes and an additional intermediate gear stages zw_9 who is used for circuitous retaining, in other forward gear, do not use this intermediate gear stages.This is outside equipped with a circuitous retaining-switching member M or N.

In pressing the 7th embodiment of Figure 13 and 14, the transmission that the 9th circuitous retaining of motility gearshift can be by the 3rd forward gear i_3, additional intermediate gear stages zw_9 and the transmission connection of the 8th forward gear i_8.Obtain almost balanced clutch load in addition because the first and the 3rd forward gear by first clutch K1 second forward gear and reversing gear connect by second clutch K2.Obtain similar clutch size thus.

At length obtain in the 7th embodiment, on the first gear plane 7-13 as bidentate wheel plane, free gear 7 is used for two forward gear G8, G9, and free gear 13 is used for a forward gear G6.On the second gear plane 8-14 as bidentate wheel plane, free gear 8 is used for a forward gear G4, and free gear 14 is used for a forward gear G2 and the R2 that reverses gear.On the 3rd gear plane 9-15 as bidentate wheel plane, free gear 9 is used for a forward gear G9 and is used for the R1 that reverses gear, and free gear 15 is used for two R1 that reverse gear, R2.On the 4th gear plane 10-16 as bidentate wheel plane, free gear 10 is used for two forward gear G3, G9 and is used for the R1 that reverses gear, and free gear 16 is used for a forward gear G1 and be used for the R2 that reverses gear.At last, on the 5th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G7, and free gear 17 is same for a forward gear G5.

In the 8th embodiment by Figure 15 and 16, obtain the transmission that the 9th circuitous retaining of motility gearshift can be by the first forward gear i_1, additional intermediate gear stages zw_9 and the transmission connection of the 8th forward gear i_8.Obtain the shift gears R1 that reverses gear of the first forward gear G1 of a motility in addition, realized freely advancing and retreat of vehicle thus.

At length obtain in the 8th embodiment, on the first gear plane 7-13 as bidentate wheel plane, free gear 7 is used for two forward gear G8, G9, and free gear 13 is used for a forward gear G6.On the second gear plane 8-14 as bidentate wheel plane, free gear 8 is used for a forward gear G4, and free gear 14 is same for a forward gear G2.On the 3rd gear plane 9-15 as bidentate wheel plane, free gear 9 is used for four R1 that reverse gear, R2, R3, R4, and free gear 15 is used for a forward gear G9 and be used for two R3 that reverse gear, R4.On the 4th gear plane 10-16 as bidentate wheel plane, free gear 10 is used for a forward gear G3 and is used for two R2 that reverse gear, R3, and free gear 16 is used for two forward gear G1, G9 and be used for two R2 that reverse gear, R4.At last, on the 5th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G7, and free gear 17 is same for a forward gear G5.

Obtain in the 9th embodiment by Figure 17 and 18, the 9th circuitous retaining of motility gearshift can be connected by the transmission of additional intermediate gear stages zw_9, the 4th forward gear i_4 and the transmission of the 8th forward gear i_8.Obtain motility in addition and shift gears the retaining C1 that creeps of the first forward gear G1 as the tenth possible forward gear, realized thus vehicle the street use and cross-country use between better transition (R2 motility shift gears G1).

At length obtain in the 9th embodiment, on the first gear plane 8-14 as bidentate wheel plane, free gear 8 is used for two forward gear G8, G9, and free gear 14 is used for a forward gear G6.On the second gear plane 9-15 as bidentate wheel plane, free gear 9 is used for three forward gear G4, G9, C1 and is used for the R1 that reverses gear, and free gear 15 is used for a forward gear G2 and with the R2 that reverses gear.On the 3rd gear plane 10-16 as bidentate wheel plane, free gear 10 is used for two forward gear G9, C1 and is used for the R1 that reverses gear, and free gear 16 is used for two R1 that reverse gear, R2.On the 4th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G7, and free gear 17 is used for a forward gear G5.At last, on the 5th gear plane 12-18 as bidentate wheel plane, free gear 12 is used for a forward gear G3, and free gear 17 is used for two forward gear G1, C1 and be used for the R2 that reverses gear.

In pressing the tenth embodiment of Figure 19 and 20, the 9th circuitous retaining of motility gearshift can be connected by the transmission of additional intermediate gear stages zw_9, the second forward gear i_2 and the transmission of the 8th forward gear i_8.Obtain shift gears overgear O1 the 9th forward gear as an alternative of the 8th forward gear G8 of a motility in addition, obtain conservation of fuel thus.In addition, the shift gears retaining of creeping of first forward gear of two motilities can be used as the tenth possible forward gear and realizes, obtains better transition between street and cross-country use thus in vehicle.

At length obtain in the tenth embodiment, on the first gear plane 8-14 as bidentate wheel plane, free gear 8 is used for three forward gear G8, G9, O1, and free gear 14 is used for a forward gear G6.On the second gear plane 9-15 as bidentate wheel plane, free gear 9 is used for three forward gear G4, C1, O1 and is used for the R2 that reverses gear, and free gear 15 is used for three forward gear G2, G9, C2 and is used for the R3 that reverses gear.On the 3rd gear plane 10-16 as bidentate wheel plane, free gear 10 is used for three forward gear G5, C1, O1 and is used for the R2 that reverses gear, and free gear 16 is used for two forward gear G9, C2 and be used for the R3 that reverses gear.On the 4th gear plane 11-17 as bidentate wheel plane, free gear 11 is used for a forward gear G3, and free gear 17 is used for three forward gear G1, C1, C2.At last, on the 5th gear plane 12-18 as bidentate wheel plane, free gear 12 is used for a forward gear G7, and free gear 18 is used for three reverse gear R1, R2, R3.

In all embodiments of dual-clutch transmission, repeatedly utilize each free gear owing to set, thereby under the identical situation of retaining number, need less gear plane and the less member of needs, therefore advantageously saved structure space and cost.

Irrelevant with each embodiment, meaning that by the numeral " 1 " in the zone of the corresponding grid of Fig. 2,4,6,8,10,12,14,16,18 and 20 gearshift figure clutch K1, the K2 that sets or coupling A, B, C, D, E, F, G, H, I, J, K, the L that sets or the switching member M, the N that set are closed respectively.And mean that at the white space by the corresponding grid of Fig. 2,4,6 and 8 gearshift figure clutch K1, the K2 that sets or coupling A, B, C, D, E, F, G, H, I, J, K, the L that sets or the switching member M, the N that set open respectively.In addition, have such possibility in many cases, insert other coupling element or switching member, and influence power does not flow.Can realize the gear preliminary election thus.

List of numerals

The fixed gear of 1 second transmission input shaft

The fixed gear of 2 second transmission input shafts

The fixed gear of 3 second transmission input shafts

The fixed gear of 4 first transmission input shafts

The fixed gear of 5 first transmission input shafts

The fixed gear of 6 first transmission input shafts

The free gear of 7 first jack shafts

The free gear of 8 first jack shafts

The free gear of 9 first jack shafts

The free gear of 10 first jack shafts

The free gear of 11 first jack shafts

The free gear of 12 first jack shafts

The free gear of 13 second jack shafts

The free gear of 14 second jack shafts

The free gear of 15 second jack shafts

The free gear of 16 second jack shafts

The free gear of 17 second jack shafts

The free gear of 18 second jack shafts

The fixed gear of 19 driven shafts

The output gear of 20 first jack shafts

The output gear of 21 second jack shafts

22 torshional vibration dampers

The K1 first clutch

The K2 second clutch

The w_an live axle

The w_ab driven shaft

W_v1 first jack shaft

W_v2 second jack shaft

W_k1 first transmission input shaft

W_k2 second transmission input shaft

The A coupling

The B coupling

The C coupling

The D coupling

The E coupling

The F coupling

The G coupling

The H coupling

The I coupling

The J coupling

The K coupling

The L coupling

The gear stage of i_1 first forward gear

The gear stage of i_2 second forward gear

The gear stage of i_3 the 3rd forward gear

The gear stage of i_4 the 4th forward gear

The gear stage of i_5 the 5th forward gear

The gear stage of i_6 the 6th forward gear

The gear stage of i_7 the 7th forward gear

The gear stage of i_8 the 8th forward gear

The gear stage of i_9 the 9th forward gear

Zw_9 intergrade gear

G1 first forward gear

G2 second forward gear

G3 the 3rd forward gear

G4 the 4th forward gear

G5 the 5th forward gear

G6 the 6th forward gear

G7 the 7th forward gear

G8 the 8th forward gear

G9 the 9th forward gear

The C1 retaining of creeping

The C2 retaining of creeping

The O1 overgear

The O2 overgear

The O3 overgear

The O4 overgear

The O5 overgear

R1 reverses gear

R2 reverses gear

R3 reverses gear

R4 reverses gear

The w_zw countershaft

The ZR intermediate gear

The gear stage that ZS uses

The M switching member

The N switching member

Lsb. motility gearshift

Claims

1. dual-clutch transmission, comprise: two clutches (K1, K2), the input side of described two clutches be connected with a live axle (w_an) and the outlet side of described two clutches respectively with two transmission input shafts (w_k1, w_k2) that arrange coaxially with each other in one be connected; Two jack shafts (w_v1, w_v2), the shift gear that constitutes free gear (7,8,9,10,11,12,13,14,15,16,17,18) can be rotated to support on the described jack shaft; Rotationally fixedly is arranged on described two transmission input shafts (w_k1, w_k2) and goes up and constitute shift gear fixed gear (1,2,3,4,5,6), at least part of and free gear (7,8,9,10,11,12,13,14,15,16,17,18) engagement; A plurality of be used to the coupling (A, B, C, D, E, F, G, H, I, J, K, L) that free gear (7,8,9,10,11,12,13,14,15,16,17,18) is connected with jack shaft (w_v1, w_v2) rotationally fixedly; Be arranged on each output gear (20,21) on two jack shafts (w_v1, w_v2), this output gear correspondingly is coupled with the tooth portion of a driven shaft (w_ab); And at least one is used for the switching member (M that rotationally fixedly connects two shift gears, N), wherein can connect the forward gear (G1 of a plurality of motility gearshifts, G2, G3, G4, G5, G6, G7, G8, G9) and at least one (R1 that reverses gear, R2, R3, R4), it is characterized in that, five gear planes are set, at least four bidentate wheel plane (7-13 wherein are set, 8-14,9-15,10-16,11-17,12-18), and at each bidentate wheel plane (7-13,8-14,9-15,10-16,11-17, first and second jack shaft (the w_v1 12-18), w_v2) each free gear (7,8,9,10,11,12,13,14,15,16,17,18) be equipped on described transmission input shaft (w_k1, w_k2) one of a fixed gear (1,2,3,4,5,6), wherein at each bidentate wheel plane (7-13,8-14,9-15,10-16,11-17, at least one free gear (8 12-18), 9,10,11,14,15,16,17,18) can be used at least two gears, make the circuitous retaining of at least one motility gearshift can pass through described at least one switching member (M, N) connect.

2. by the described dual-clutch transmission of claim 1, it is characterized in that: five bidentate wheel planes (8-14,9-15,10-16,11-17,12-18) are set.

3. by the described dual-clutch transmission of claim 1, it is characterized in that: four bidentate wheel planes (7-13,8-14,9-15,10-16,11-17,12-18) and an individual gears plane (1-13,7-1,2-14,10-4,6-18) are set.

4. by the described dual-clutch transmission of claim 1, it is characterized in that: by the switching member (M) on first jack shaft (w_v1), the free gear (9) of second speed changer part can be connected with the free gear (10) of first speed changer part, makes by should connecting first forward gear (G1) and the circuitous retaining of at least one overgear (O1, O2) conduct by the switching member (M) on first jack shaft (w_v1).

5. by each described dual-clutch transmission in the claim 1 to 3, it is characterized in that: by the switching member (M) on first jack shaft (w_v1), the free gear (9) of second speed changer part can be connected with the free gear (10) of first speed changer part, makes by should connecting the 9th forward gear (G9) and at least one circuitous retaining of (R1) conduct that reverses gear by the switching member (M) on first jack shaft (w_v1).

6. by the described dual-clutch transmission of claim 1, it is characterized in that: by the switching member (N) on second jack shaft (w_v2), the free gear (15) of second speed changer part can be connected with the free gear (16) of first speed changer part, makes that the 9th forward gear (G9) and one are reversed gear (R2, R3, R4) and/or the retaining of creeping (C1, C2) conduct makes a circulation to keep off by should the switching member (N) on second jack shaft (w_v2) connecting.

7. by each described dual-clutch transmission in the claim 1 to 3, it is characterized in that: be included in two fixed gears (2,3) on second speed changer, second transmission input shaft (w_k2) partly as the first gear plane (8-14) on bidentate wheel plane and the second gear plane (9-15).

8. by each described dual-clutch transmission in the claim 1 to 3, it is characterized in that: as the 3rd gear plane (10-16) on bidentate wheel plane or as the 3rd gear plane (10-4) on individual gears plane, as the 4th gear plane (11-17) on bidentate wheel plane with as the 5th gear plane (12-18) on bidentate wheel plane or be included in three fixed gears (4,5,6) on first transmission input shaft (w_k1) of first speed changer part as the 5th gear plane (6-18) on individual gears plane.

9. by each described dual-clutch transmission in the claim 1 to 3, it is characterized in that: as the first gear plane (7-13) on bidentate wheel plane or as the first gear plane (1-13 on individual gears plane; 7-1), as the second gear plane (8-14) on bidentate wheel plane or as the second gear plane (2-14) on individual gears plane be included in three fixed gears (1,2,3) on second transmission input shaft (w_k2) of second speed changer part as the 3rd gear plane (9-15) on bidentate wheel plane.

10. by each described dual-clutch transmission in the claim 1 to 3, it is characterized in that: as the 4th gear plane (10-16) on bidentate wheel plane with comprise two fixed gears (4,5) of first transmission input shaft (w_k1) of first speed changer part as the 5th gear plane (11-17) on bidentate wheel plane.

11. by claim 1 or 3 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be by first clutch (K1) and coupling (I) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (C) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (E) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (B) that is activated, and the 9th forward gear (G9) can be connected by first clutch (K1) with by the coupling (L) that is activated, and/or one reverse gear (R1) can connect by first clutch (K1) with by the coupling (J) that is activated.

12. by the described dual-clutch transmission of claim 11, it is characterized in that: an overgear (O1) can be by second clutch (K2), coupling (L) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining.

13. by claim 1 or 3 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be by first clutch (K1) and coupling (G) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (G) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (J) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (C) that is activated, and the 9th forward gear (G9) can be connected by first clutch (K1) with by the coupling (E) that is activated, and/or one reverse gear (R1) can be by first clutch (K1) and coupling (A) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining.

14. by the described dual-clutch transmission of claim 13, it is characterized in that: the retaining (C1) of creeping can be by first clutch (K1) and coupling (G) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining, and/or an overgear (O1) can be by second clutch (K2) and coupling (E) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or another overgear (O2) can be by second clutch (K2) and coupling (K) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or next overgear (O3) can be by second clutch (K2) and coupling (E) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining, and/or another overgear (O4) can connect by second clutch (K2) with by the coupling (D) that is activated and by the switching member (N) on second jack shaft (w_v2) that is activated as circuitous retaining, and/or another overgear (O5) can be by second clutch (K2) and coupling (K) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous the retaining.

15. by claim 1 or 3 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (E) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (B) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (L) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (C) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (I) that is activated, and the 9th forward gear (G9) can be connected by first clutch (K1) with by the coupling (I) that is activated and the switching member (M) on first jack shaft (w_v1) that passes through activation as circuitous retaining, and/or one reverse gear (R1) can be by second clutch (K2) and coupling (F) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous the retaining.

16. by claim 1 or 3 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (E) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (C) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (J) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (G) that is activated, and the 9th forward gear (G9) can be by first clutch (K1) and coupling (G) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining, and/or one reverse gear (R1) can connect by second clutch (K2) with by the coupling (B) that is activated, and/or another reverse gear (R2) can be by first clutch (K1) and coupling (B) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining.

17. by the described dual-clutch transmission of claim 16, it is characterized in that: the retaining (C1) of creeping keeps off by second clutch (K2) and coupling (E) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous, and/or an overgear (O1) can be by first clutch (K1) and coupling (G) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining.

18. by claim 1 or 3 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (L) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (B) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (E) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (J) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (C) that is activated, and the 9th forward gear (G9) can be connected by first clutch (K1) with by the coupling (C) that is activated and by the switching member (N) on second jack shaft (w_v2) that is activated as circuitous retaining, and/or one reverse gear (R1) can be by second clutch (K2) with by the coupling (L) that is activated and switching member (M) connection on first jack shaft (w_v1) of passing through activation as circuitous retaining.

19. by the described dual-clutch transmission of claim 18, it is characterized in that: the retaining (C1) of creeping can be by second clutch (K2) and coupling (L) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining.

20. by claim 1 or 3 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (E) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (C) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (J) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (A) that is activated, and the 9th forward gear (G9) can be by first clutch (K1) and coupling (A) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining, and/or one reverse gear (R1) can connect by second clutch (K2) with by the coupling (B) that is activated, and/or another reverse gear (R2) can be by first clutch (K1) and coupling (B) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining.

21. by the described dual-clutch transmission of claim 20, it is characterized in that: the retaining (C1) of creeping can be connected by second clutch (K2) with by the coupling (E) that is activated and by the switching member (M) on first jack shaft (w_v1) that is activated as circuitous retaining, and/or another retaining (C2) of creeping keep off as making a circulation can be by second clutch (K2) and coupling (E) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated.

22. by claim 1 or 2 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (J) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (B) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (G) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (E) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (A) that is activated, and the 9th forward gear (G9) can be by first clutch (K1) and coupling (A) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or one reverse gear (R1) can connect by first clutch (K1) with by the coupling (I) that is activated and by the switching member (M) on first jack shaft (w_v1) that is activated as circuitous retaining, and/or another reverse gear (R2) can be by first clutch (K1) and coupling (H) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous the retaining.

23. by claim 1 or 2 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (J) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (B) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (G) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (E) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (A) that is activated, and the 9th forward gear (G9) can be connected by first clutch (K1) with by the coupling (A) that is activated and the switching member (N) on second jack shaft (w_v2) that is activated as circuitous retaining, and/or one reverse gear (R1) can connect by second clutch (K2) with by the coupling (C) that is activated, and/or another reverse gear (R2) can be by second clutch (K2) and coupling (J) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or another reverse gear (R3) can connect by first clutch (K1) with by the coupling (I) that is activated and by the switching member (M) on first jack shaft (w_v1) that is activated as circuitous retaining, and/or the next one reverse gear (R4) can be by first clutch (K1) and coupling (C) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous the retaining.

24. by claim 1 or 2 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (L) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (F) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (C) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (K) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (E) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (B) that is activated, and the 9th forward gear (G9) can be by first clutch (K1) and coupling (B) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or one reverse gear (R1) can connect by second clutch (K2) with by the coupling (J) that is activated and the switching member (M) on first jack shaft (w_v1) that passes through to activate as circuitous retaining, and/or another reverse gear (R2) can connect by second clutch (K2) and the coupling that is activated (L) and by the switching member (N) on second jack shaft (w_v2) that is activated as circuitous retaining, and/or retaining (C1) conduct of creeping make a circulation to keep off can be by second clutch (K2) and coupling (L) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated.

25. by claim 1 or 2 described dual-clutch transmissions, it is characterized in that: first forward gear (G1) can be connected by first clutch (K1) with by the coupling (K) that is activated, second forward gear (G2) can be connected by second clutch (K2) with by the coupling (I) that is activated, the 3rd forward gear (G3) can be connected by first clutch (K1) with by the coupling (E) that is activated, the 4th forward gear (G4) can be connected by second clutch (K2) with by the coupling (C) that is activated, the 5th forward gear (G5) can be connected by first clutch (K1) with by the coupling (D) that is activated, the 6th forward gear (G6) can be connected by second clutch (K2) with by the coupling (H) that is activated, the 7th forward gear (G7) can be connected by first clutch (K1) with by the coupling (F) that is activated, the 8th forward gear (G8) can be connected by second clutch (K2) with by the coupling (B) that is activated, and the 9th forward gear (G9) can be by first clutch (K1) and coupling (B) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining, and/or one reverse gear (R1) can connect by first clutch (K1) with by the coupling (L) that is activated, and/or another reverse gear (R2) can be by second clutch (K2) and coupling (L) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or another reverse gear (R3) can be by second clutch (K2) and coupling (L) and switching member (N) connection on second jack shaft (w_v2) by being activated by being activated as circuitous retaining, and/or the retaining (C1) of creeping can be by second clutch (K2) and coupling (K) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous retaining, and/or another retaining (C2) of creeping can connect by second clutch (K2) with by the coupling (K) that is activated and by the switching member (N) on second jack shaft (w_v2) that is activated as circuitous retaining, and/or an overgear (O1) can be by first clutch (K1) and coupling (B) and switching member (M) connection on first jack shaft (w_v1) by being activated by being activated as circuitous the retaining.